US20190015838A1 - Impact bar - Google Patents
Impact bar Download PDFInfo
- Publication number
- US20190015838A1 US20190015838A1 US16/010,048 US201816010048A US2019015838A1 US 20190015838 A1 US20190015838 A1 US 20190015838A1 US 201816010048 A US201816010048 A US 201816010048A US 2019015838 A1 US2019015838 A1 US 2019015838A1
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- impact bar
- longitudinal ribs
- rotor
- impact
- flank
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- 238000009434 installation Methods 0.000 claims abstract description 19
- 230000005540 biological transmission Effects 0.000 claims abstract description 9
- 230000001681 protective effect Effects 0.000 claims description 10
- 230000007704 transition Effects 0.000 claims description 8
- 230000002441 reversible effect Effects 0.000 claims description 7
- 239000000463 material Substances 0.000 description 25
- 230000000694 effects Effects 0.000 description 6
- 238000004519 manufacturing process Methods 0.000 description 4
- 229910052500 inorganic mineral Inorganic materials 0.000 description 3
- 239000011707 mineral Substances 0.000 description 3
- 230000002829 reductive effect Effects 0.000 description 3
- 230000008901 benefit Effects 0.000 description 2
- 238000005266 casting Methods 0.000 description 2
- 230000003313 weakening effect Effects 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 238000004873 anchoring Methods 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 239000000919 ceramic Substances 0.000 description 1
- 229910010293 ceramic material Inorganic materials 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000003292 diminished effect Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000002708 enhancing effect Effects 0.000 description 1
- 230000003116 impacting effect Effects 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 238000004064 recycling Methods 0.000 description 1
- 230000008439 repair process Effects 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 239000004575 stone Substances 0.000 description 1
Images
Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
- B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
- B02C13/00—Disintegrating by mills having rotary beater elements ; Hammer mills
- B02C13/26—Details
- B02C13/28—Shape or construction of beater elements
- B02C13/2804—Shape or construction of beater elements the beater elements being rigidly connected to the rotor
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
- B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
- B02C13/00—Disintegrating by mills having rotary beater elements ; Hammer mills
- B02C13/02—Disintegrating by mills having rotary beater elements ; Hammer mills with horizontal rotor shaft
- B02C13/06—Disintegrating by mills having rotary beater elements ; Hammer mills with horizontal rotor shaft with beaters rigidly connected to the rotor
Definitions
- the invention relates to an impact bar for an impact crusher with the features of claim 1 , and to a rotor with such an impact bar according to the features of claim 8 as well as to an impact crusher according to claim 14 .
- Impact crushers are used for comminuting mineral materials (natural stone or recycling material) and for the production of fine or coarse aggregate. For this purpose, the material is moved in free fail to the effective region of impact bars of a rotor and hurled from there against impact plates. It is smashed there. The impact bars represent wearing parts and must be replaced periodically. Reversible impact crushers permit a change in the rotation direction of the rotor, so that the front and backsides of the impact bars can be used alternatingly, until the wear limit has been reached. Thereafter, the impact bars can be turned about their own length axis.
- An end zone of the impact bars that has not yet worn off and is located in an impact bar mount in the rotor thus advances outwards, so that the impact bar can be used until also this end zone reaches the wear limit.
- the holding region is too small, the impact bar may be exposed to high stress. The impact bar may break, causing damage to further parts of the impact crusher. Repair works and production downtimes are the result.
- the holding region is too large, significant material parts of the impact bar may not be used for contact with the material to be comminuted. A low utilization factor is not economically viable.
- the invention is based on the object to provide for an impact crusher an impact bar which has a long service life and high utilization factor.
- an appropriate rotor shall be provided for such an impact bar as well as an impact crusher with a rotor having longer service life.
- the first object is achieved by an impact bar with the features of claim 1 .
- a suitable rotor, which achieves this object, is subject matter of patent claim 8 and a respective impact crusher is subject matter of claim 14 .
- a turnable impact bar is proposed for use in an axis-parallel impact bar mount of an especially reversible rotor of an impact crusher.
- a maximum utilization factor is established when the impact bar can be turned.
- the impact bar includes a holding region in the middle and respective impact zones adjacent to the holding region.
- One of the two impact zones at the end faces of an impact bar is situated in a use position, i.e. it projects beyond the rotor.
- the other impact zone is situated in the rotor in a protected manner and may be transferred to the use position by turning the impact bar.
- the impact bar has within a Cartesian coordinate system a longitudinal axis which extends in z direction in parallel relation to the impact bar mount of the rotor, when assuming the installation position, a vertical axis which extends in y direction and is directed towards a radial head face of the impact bar, and a transverse axis which extends in x direction and is directed towards a length side of the impact bar.
- the origin of this coordinate system is located in the middle of the cross sectional area of the impact bar.
- the impact bar includes on each of its length sides (front side and backside) two terminal end faces which provide impact surfaces, and a front-side and a rear-side holding region between the end faces. Which side is the front side and which side is the backside depends on the installation position and on the rotation direction of the rotor.
- the invention is based on identical front and backsides in relation to the effective areas there. This enables a reversible operation of the rotor, without the reversal of the impact bar requiring a turning thereof by hand.
- the holding regions are bordered by two identical longitudinal ribs, respectively, i.e. the holding regions are situated between the longitudinal ribs.
- the longitudinal ribs project beyond the end faces.
- the longitudinal ribs are mirror images of one another in relation to the y-z plane and to the x-z plane.
- the impact bar is rotationally symmetrical as a result. It can be turned by 180° about the x, y, or z axis and thus forms an image of itself.
- the longitudinal ribs have a trapezoidal cross section. They have a broad base on the impact bar and a narrower topside at a distance to the base. The topside extends parallel to the y-z plane. Also the end faces extend substantially parallel to the y-z plane. “Substantially” relates in this context “within the scope of manufacturing tolerances”.
- the impact bar may involve in particular a cast part. Cast parts have surfaces which for manufacturing reasons are slightly inclined or uneven.
- the invention covers surfaces, which are produced through casting, as well as surfaces which underwent forming or material removing processes, e.g. forged or milled surfaces.
- the impact bar according to the invention can be made of a metallic cast material, a ceramic material, or a hybrid material of steel with ceramic proportions. The invention is not limited to a particular material, so long as this material is able to crush mineral material with sufficient service life.
- the trapezoidal longitudinal ribs have each two flanks which extend from the base to the topside.
- the confronting inner flanks of adjacent longitudinal ribs define a flank angle of 20° to 27° in relation to the x axis.
- the flank angle is 23° to 26° and preferably 25°. This flank angle has proven to be especially appropriate for the transmission of forces from the impact bar onto the rotor and for the transmission of the torque from the rotor onto the impact bar.
- flank angles of both inner flanks are identical but also the flank angles of both outer flanks.
- flank angles of the inner and outer flanks can be identical and also amount to 20° to 27°, in particular 23° to 26°, preferably 25°.
- the outer flanks have this angle that deviates by approx. 25° from the x axis so that the forces introduced into the longitudinal ribs have to be deflected at the transition from the base to the flanks not by 90° but rather by about 65°.
- the transitions of the flanks to the base are rounded, a fact that also prevents stress peaks in the material.
- the impact bar has a width which is measured in x direction and is at least as great between the longitudinal ribs as the width in the region of the end faces.
- the width between the longitudinal ribs is greater than the width in the region of the end faces, in particular in the magnitude of 4 to 10%.
- the width of the impact bar in the impact zone deviates only relatively slightly from the width between the longitudinal ribs, e.g. 80 mm/85 mm or 100 mm/108 mm (width end faces/width between the longitudinal ribs).
- the greater width between the longitudinal ribs is appropriate because the longitudinal ribs are exposed to higher loads, when the force is introduced in the manner according to the invention and because the loads on the longitudinal ribs should be transmitted onto the further longitudinal ribs via the central region of the impact bar with as little stress as possible.
- the central region of the impact bar between the longitudinal ribs should therefore have a greater width.
- the invention is based on the fact that the width of an impact bar that is not worn off is substantially constant in both the region of the end faces and between the longitudinal ribs.
- the holding region relates within the scope of the invention to the one region in which the impact bar is clamped. It begins on an upper contact zone at the outer longitudinal rib and ends on a lower contact zone at the lower longitudinal rib. The impact bar is clamped between the longitudinal ribs through formfitting engagement.
- the invention avoids a weakening of the cross section of the impact bar as a result of lateral notches.
- the provision of more material in the central region creates the basis for a secure anchoring of a turnable impact bar.
- the combination of the slightly wider central region with these flank angles of the inner flanks enables an impact bar which requires as a result less material while having higher stress resistance and therefore attains a high utilization factor of at least 50%.
- the utilization factor is greater than 55% and in particular greater than 60%.
- the confronting inner flanks of the longitudinal ribs are shorter than the outer flanks, so long as the inner and outer flanks have the same flank angle.
- centrifugal forces are transmitted via the inner flanks of the radially inner longitudinal ribs onto the impact bar clamps in the impact bar mount.
- the impact bars effect very high centrifugal forces due to their high own weight and high rotation speeds.
- the formfitting engagement between rotor and impact bars effects a secure fixation in radial direction of the rotor.
- the impact bars can be replaced at standstill in a mechanically simple manner because of their sole contact with the rotor via the flanks of the longitudinal ribs.
- the impact bars may be pulled out of the impact bar mounts.
- simple fixing means are sufficient to effect the axial securement, such as, e.g. axial safeguards that are screwed onto the rotor. They are easy to detach and enable a direct access to the impact bar.
- the impact bar mount is bordered on both sided by impact bar clamps.
- the impact bar clamps are welded to the rotor.
- the rotor may be constructed from several rotor disks arranged in parallel relationship, with the impact bar clamps extending from rotor disk to rotor disk.
- the impact bar clamps are those components with which the impact bars are in contact via their flanks.
- the inner flanks of the radially inner longitudinal ribs are not exposed to stress by the centrifugal forces but primarily by the fact that the material to be comminuted impacts the impact bar and is greatly accelerated by the impact bar. As the impact circle of the rotor is greater than the rotor itself, torque is exerted upon the impact bar. This torque is transmitted via the flanks of the longitudinal ribs into the rotor. Conversely, the driven rotor transmits forces into the impact bar clamps which in turn transmit the forces via these flanks into the longitudinal ribs of the impact bar.
- the inner confronting flanks of the longitudinal ribs are in addition to the impact surfaces the most important surfaces of the impact bars as they, and only they in accordance with the invention, participate in the force transmission. It is not excluded within the scope of the invention for the mineral material that has penetrated gaps and joints between impact bar and impact bar clamp to effect an additional or indirect force transmission. The forces are transmitted predominantly via the flanks.
- the flanks are oriented such that the torques to be absorbed impact about the longitudinal axis (rotation axis/z axis) onto surfaces which extend in radial direction towards the rotation axis. Ideally is when these surfaces are spaced at great radial distance to the rotation axis.
- the lever arm is increased and as a result surface pressure is reduced at the support point, i.e. the force vector becomes smaller.
- the inner flanks are arranged virtually x-shaped in relation to the center point of the impact bar or z axis, about which the torque is applied and which lie in the same plane in which the diametrically arranged inner flanks are located.
- the introduced torques are absorbed in this configuration by the impact bar clamps in an optimum manner. Bending moments in the longitudinal ribs are reduced and wear as well as material stress are diminished. Risk of breakage decreases so that the central region between the longitudinal ribs can be configured smaller in relation to the overall impact bar, thereby enhancing the utilization factor.
- both radially outer flanks can form a shoulder for protection of adjacent components of the rotor.
- the radially outer flanks may for this purpose wear off to a certain degree. This does not adversely affect the function of the impact bar because the outer flanks have no contact areas with the rotor. A deviation of the dimensional precision or wear in this region does not impair the secure fit or service life of the impact bar.
- a geometry of the impact bar is viewed as especially beneficial, when the ratio between the width of the impact zone and the minimum distance of the flanks in the central region is 1.8-2.2 to 1, in particular 2 to 1.
- This width in the impact zone is preferably greater than 70 to 80 mm.
- the width is in particular constant across the entire impact zone.
- the ratio between the minimum distance of the inner flanks between the longitudinal ribs and the height of the longitudinal ribs is preferably 1.8-2.2 to 1, in particular 2 to 1.
- the longitudinal ribs should have a width in x direction of 40%-60%, in particular 50%, in relation to the height of the impact bar. Their topsides should have a height in y direction of preferably 40%-60%, in particular 50%, in relation to the minimum distance of the inner flanks between the longitudinal ribs.
- the width of the impact bar in the region of the longitudinal ribs is greater by preferably 40%-60%, in particular 50%, than the width of the impact bar in the impact zone.
- the length of the impact bar in z direction is independent on other proportions.
- the invention proposes for securement an appropriate rotor in which the impact bar mount includes opposing impact bar clamps with projections in order to engage between the longitudinal ribs.
- the projections have in this case the same flank angles as the inner flanks of the longitudinal ribs.
- the surface pressure is kept as small as possible, that is on both the rotor and the impact bar.
- the material is used in an optimum manner while stress is even. Thus, material can be saved on the rotor and on the impact bar.
- protective rotor plates are arranged on the rotor to radially cover the impact bar clamps about their circumference.
- the protective rotor plates are replaceable wear parts, which, however, have a much longer service life than the impact bars, because they are exposed to less stress.
- the protective rotor plates can be placed in accordance with the invention in very close proximity to the impact bar.
- a border side of a protective rotor plate is arranged preferably directly in opposition to the topsides of the radially outer longitudinal ribs.
- the contact zone between the impact bar and the impact bar clamps is very limited in height.
- the radially innermost contact zones between the impact bar and the impact bar clamps are situated at the inner flanks of the radially inner longitudinal ribs.
- the radially outermost contact zones between the impact bar and the impact bar clamp are situated at the inner flank of the radially outer longitudinal ribs.
- the impact bar mount can include a radially inner region for receiving the second end face or second impact section of the impact bar, with this region widening in x direction, and a region which is narrower in x direction and situated between the projections. It is located further radially outwards.
- a rounded transition zone is arranged between these regions and extends across at least 50% of the width of the topside of the inner longitudinal ribs. The rounded zone is very large so as to prevent as much as possible formation of notch stress in this region.
- the topsides of the longitudinal ribs do not touch the inner regions of the impact bar mount and therefore do not transmit any forces. In view of the longitudinal ribs that directly confront one another in pairs, broad shoulder belts are established which transmit the centrifugal forces of the impact bar into the rotor.
- the confronting radially outer longitudinal ribs form a region of maximum width as shoulder belt.
- the greatest torques of the impact bar are applied at the radially outer shoulder belt. They are effectively introduced into the adjacent regions as a result of the optimized flank geometries.
- the broad shoulder also protects the rotor itself even against wear.
- the impact bar is profiled in a simple manner, has clear proportions and therefore is cost-effectively to produce.
- the impact bar has a greatest possible support width due to the diametrically arranged flanks of orientation in same direction, so that stress on the impact bar is reduced.
- the greatest possible radius in the impact bar mount prevents stress peaks in the impact bar clamp and provides highest stability.
- the flank angle of approx. 20 to 27°, preferably 25°, has the advantage that the deflection forces within the impact bar mount are small. As the flank angle increases, also the deflection forces would increase, i.e. the forces that act transversely to the impact bar mount. Flank angles below 20° would enlarge the width of the impact bar, when the radial distance of the flanks remains the same, thereby decreasing the utilization factor. When the width should not be made greater, the radial distance of the flanks needs to be made smaller, resulting in shorter lever arms and higher surface pressure. The range between 20′ and 27° has been viewed as optimal.
- the rotor may be equipped with two, three or more identical impact bars which are evenly dispersed about the circumference. It is also possible to combine impact bars of different height, e.g. two impact bars of greater height with two impact bars of smaller height in alternating disposition.
- the impact bars find application in particular in reversible impact crushers. Use in non-reversible impact crushers is also possible.
- FIG. 1 a plan view of a rotor of an impact crusher
- FIG. 2 a section through the rotor of FIG. 1 along the line II of FIG. 1 ;
- FIG. 3 a detail III of FIG. 3 ;
- FIG. 4 a cross section of an impact bar.
- FIG. 1 shows a rotor 1 of an otherwise not shown impact crusher.
- the rotor 1 includes a horizontal rotor shaft 2 which is mounted in bearings 3 , 4 .
- the rotor shaft 2 extends horizontally between the bearings 3 , 4 and is driven by a pulley 5 .
- Impact bars 6 are dispersed about the circumference of the rotor 1 .
- the uppermost impact bar 6 in the drawing plane of FIG. 1 extends like all other impact bars 6 in parallel relation to the rotation axis D of the rotor shaft 2 .
- the following description of the impact bars 6 relates to a Cartesian coordinate system.
- the origin of the coordinate system is situated in the middle of the impact bar 6 , i.e. at half length (z axis), height (y axis) and width (x axis) of this impact bar 6 .
- the x direction extends tangentially to the rotor 1 .
- the y axis is the radial direction and points away from the rotor shaft 2 .
- the z axis extends parallel to the rotation axis D.
- a total of four impact bars 6 are evenly dispersed about the circumference of the rotor 1 .
- the four impact bars 6 are identical, as are the associated impact bar mounts 7 within the rotor 1 .
- the impact bar mounts 7 represent pockets that extend in length direction of the rotor, i.e. parallel to the rotation axis D of the rotor shaft 2 . With reference to the coordinate system introduced in FIG. 1 , the pockets extend in z direction.
- the impact bars 6 are configured in cross section substantially rectangular. With reference to the y-z plane and also with reference to the x-z plane, the impact bars are mirror images. They have each radial head faces which extend in substantial parallel relation to the x-z plane. As the impact bars 6 involve cast parts, the head faces 8 may have a slight draft as caused by casting. The length sides 9 , 10 of the impact bar 6 extend at a parallel distance to one another and as a result extend substantially perpendicular to the head faces 8 .
- Two terminal end faces 11 , 12 , 13 , 14 are situated at the length sides 9 , 10 and provide impact surfaces.
- the holding regions 15 , 16 are respectively limited by two longitudinal ribs 17 , 18 , 19 , 20 as is apparent also by the illustration of FIGS. 2 to 4 .
- All longitudinal ribs 17 - 20 are of identical configuration and have the same cross section.
- the longitudinal ribs 17 - 20 have a trapezoidal cross section and a have a wider base 21 and a narrower topside 22 ( FIG. 4 ).
- Inclined flanks extend between the base 21 and the topside 22 .
- Inner flanks 23 - 26 confront one another and limit the holding regions 15 , 16 .
- Outer flanks 27 form the transition to the end faces 11 - 14 . All edges are rounded.
- Arrow P 1 in FIG. 2 symbolizes the rotation direction of the rotor shaft 2 and thus of the rotor 1 . Due to the rotation direction, the end face 11 represents the impact surface that is subject to stress. At this rotation direction, also the designations front side and backside of the impact bar 6 could be used. As the rotation direction is reversible, the opposite end face 14 may likewise serve as impact surface, when operation is reversed.
- a rotary movement is transmitted via the rotor 1 and the impact bar mounts 17 onto the impact bars 6 .
- the impact bars 6 are pushed into the impact bar mounts 7 in a manner not shown in greater detail in z direction, i.e. in length direction of the rotor 1 .
- the impact bars are secured in the installation position against axial displacement.
- the impact bar clamps 28 , 29 rest upon the inner flanks 23 - 26 of the impact bar 6 , respectively. Due to the inclined inner flanks 23 - 26 , the undercut region, i.e. the respective holding region 15 , 16 , has a trapezoidal cross section with rounded corners.
- a contact zone is established between the flanks 23 - 26 and the impact bar clamps 28 , 29 .
- the impact bar clamps 28 , 29 have for that purpose opposing identical projections 30 , 31 with a geometry and in particular with support faces which conform to the flank angles of the inner flanks 23 - 26 .
- the flank angle W 1 is depicted in FIG. 4 .
- FIG. 3 shows that the radially outermost contact zone between the impact bar clamps 28 , 29 and the impact bar 6 is formed by the radially inner flanks 23 , 24 of the radially outer longitudinal ribs 17 , 19 .
- the radially innermost contact zones are located between the inner flanks 25 , 26 and the respective projections 30 , 31 of the impact bar clamps 28 , 29 .
- the radial outer longitudinal ribs 17 , 19 project beyond the impact bar clamps 28 , 29 and radially rest virtually from outside against the rotor 1 . They are protected by protective rotor plates 32 which are screwed onto the rotor 1 radially from outside.
- the protective rotor plates 32 cover the impact bar clamps 28 , 29 and protect them against wear.
- the protective rotor plates 32 have each a border side 33 which confronts the topsides 22 of the longitudinal ribs 17 , 19 . In this way, the longitudinal ribs 17 , 19 are protected in this region against wear.
- the protective rotor plates 32 are detachably secured.
- FIG. 3 shows an enlarged view of the area Ill according to FIG. 2 .
- Various wear lines are plotted in the radially outer part of the impact bar 6 .
- the wear lines show that the rotor 1 has been operated at the beginning counterclockwise, since the left upper corner of the impact bar 6 has been stripped off at first. Subsequently, the rotation direction has been reversed, so that the end face 11 on the right-hand side of the drawing plane serves as impact surface. Thus, the right upper corner of the impact bar 6 has been stripped.
- the wear limit V has been reached.
- the wear limit V is located approximately in prolongation of the radially outer flanks 27 .
- the wear limit V is the limit for maximum use of the impact bar 6 .
- the impact bar 6 has in this state an approximately triangular remaining cross section at the wear limit V.
- the impact bar 6 When the wear limit V has ultimately been reached, the impact bar 6 is pulled out of the impact bar mount 7 in length direction of the rotor 1 and can be turned about its length axis, so that the previously inner end faces 13 , 14 now face outwards. There is no preferential direction of the impact bar 6 , when turning by 180 degrees. It is irrelevant, whether the impact bar 6 is turned about its length axis only, or turned at the same time during turning about its vertical axis. The rotational symmetry of the impact bar 6 enables both insertion directions into the impact bar mount 7 .
- FIG. 3 shows that the impact bar mount 7 is configured relatively wide in the region of the impact bar 6 that is not in engagement.
- the impact bar mount 7 there is an inner region 34 which is widened in x direction.
- the width of this inner region 34 is greater than the width of the impact bar 6 , measured across the longitudinal ribs 18 , 20 .
- a region 35 that is narrower in x direction is situated between the projections 30 , 31 .
- the wider region 34 is connected to the narrower region 35 by a transition zone 36 .
- the transition zone 36 is rounded. Rounding of the transition. zone 36 extends across at least 50% of the height of the topside 22 of the inner longitudinal ribs. The provision of the great rounding radius prevents stress in this region of the impact bar clamps 28 , 29 .
- the impact bar according to the invention includes for this purpose special proportions which will be described hereinafter with reference to FIG. 4 .
- the impact bar 6 includes in this exemplary embodiment a height H 1 of 320 mm at a width B 1 in its impact zone of 80 mm.
- the ratio of height to width is 4:1.
- the impact bar 6 is slightly wider in its mid mounting portion that is not subject to wear than in the impact zone.
- the longitudinal ribs 17 - 20 have each a height of 20 mm, measured from the terminal end faces 11 - 14 (width B 2 ).
- Their topsides 22 have a height H 2 of 20 mm.
- the height H 3 is measured at the base 21 and indicates the minimum distance of the inner flanks 23 - 26 of the longitudinal ribs 17 - 20 .
- FIG. 4 further shows that the flank angles W 1 are identical for all plotted flanks of the longitudinal ribs 17 - 20 . They amount to 25 degree.
- the inner flanks 23 - 26 extend each radially from a center point M of the impact bar 6 .
- the illustrated dash-dot lines intersect as prolongation of the respective inner flanks 23 - 26 in the center point M.
- the center point M lies on the length axis of the impact bar 6 (z axis), about which the mounted impact bar 6 can theoretically swing within the impact bar mount 7 during operation within the scope of the provided tolerances.
- FIG. 4 further shows that the width B 3 of the impact bar 6 , which is measured across the topsides 22 of the longitudinal ribs 18 , 20 , is sized 1.5 times the width B 1 of the impact bar 6 in the region of its impact zone.
- the width B 4 is sized at least as the width B 1 in the region of the end faces 11 , 12 , thereby preventing the presence of any notch as material weakening.
- the width B 4 in the region between the longitudinal ribs 17 - 20 is 85 mm as compared to 80 mm in the impact zones.
- the invention relates to an impact bar for installation in an axis-parallel impact bar mount ( 7 ) of a rotor ( 1 ) of an impact crusher with following features:
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Abstract
Description
- The invention relates to an impact bar for an impact crusher with the features of
claim 1, and to a rotor with such an impact bar according to the features ofclaim 8 as well as to an impact crusher according toclaim 14. - Impact crushers are used for comminuting mineral materials (natural stone or recycling material) and for the production of fine or coarse aggregate. For this purpose, the material is moved in free fail to the effective region of impact bars of a rotor and hurled from there against impact plates. It is smashed there. The impact bars represent wearing parts and must be replaced periodically. Reversible impact crushers permit a change in the rotation direction of the rotor, so that the front and backsides of the impact bars can be used alternatingly, until the wear limit has been reached. Thereafter, the impact bars can be turned about their own length axis. An end zone of the impact bars that has not yet worn off and is located in an impact bar mount in the rotor thus advances outwards, so that the impact bar can be used until also this end zone reaches the wear limit. In terms of the utilization factor of the used material, it is desirable to keep the holding region of the impact bars as small as possible and to keep the impact region that is exposed to wear as large as possible. However, when the holding region is too small, the impact bar may be exposed to high stress. The impact bar may break, causing damage to further parts of the impact crusher. Repair works and production downtimes are the result. When the holding region is too large, significant material parts of the impact bar may not be used for contact with the material to be comminuted. A low utilization factor is not economically viable.
- The invention is based on the object to provide for an impact crusher an impact bar which has a long service life and high utilization factor. In addition, an appropriate rotor shall be provided for such an impact bar as well as an impact crusher with a rotor having longer service life.
- The first object is achieved by an impact bar with the features of
claim 1. A suitable rotor, which achieves this object, is subject matter ofpatent claim 8 and a respective impact crusher is subject matter ofclaim 14. - A turnable impact bar is proposed for use in an axis-parallel impact bar mount of an especially reversible rotor of an impact crusher. A maximum utilization factor is established when the impact bar can be turned. The impact bar includes a holding region in the middle and respective impact zones adjacent to the holding region. One of the two impact zones at the end faces of an impact bar is situated in a use position, i.e. it projects beyond the rotor. The other impact zone is situated in the rotor in a protected manner and may be transferred to the use position by turning the impact bar.
- The impact bar has within a Cartesian coordinate system a longitudinal axis which extends in z direction in parallel relation to the impact bar mount of the rotor, when assuming the installation position, a vertical axis which extends in y direction and is directed towards a radial head face of the impact bar, and a transverse axis which extends in x direction and is directed towards a length side of the impact bar. The origin of this coordinate system is located in the middle of the cross sectional area of the impact bar.
- The impact bar includes on each of its length sides (front side and backside) two terminal end faces which provide impact surfaces, and a front-side and a rear-side holding region between the end faces. Which side is the front side and which side is the backside depends on the installation position and on the rotation direction of the rotor. The invention is based on identical front and backsides in relation to the effective areas there. This enables a reversible operation of the rotor, without the reversal of the impact bar requiring a turning thereof by hand.
- The holding regions are bordered by two identical longitudinal ribs, respectively, i.e. the holding regions are situated between the longitudinal ribs. The longitudinal ribs project beyond the end faces. The longitudinal ribs are mirror images of one another in relation to the y-z plane and to the x-z plane. The impact bar is rotationally symmetrical as a result. It can be turned by 180° about the x, y, or z axis and thus forms an image of itself.
- The longitudinal ribs have a trapezoidal cross section. They have a broad base on the impact bar and a narrower topside at a distance to the base. The topside extends parallel to the y-z plane. Also the end faces extend substantially parallel to the y-z plane. “Substantially” relates in this context “within the scope of manufacturing tolerances”. The impact bar may involve in particular a cast part. Cast parts have surfaces which for manufacturing reasons are slightly inclined or uneven. The invention covers surfaces, which are produced through casting, as well as surfaces which underwent forming or material removing processes, e.g. forged or milled surfaces. The impact bar according to the invention can be made of a metallic cast material, a ceramic material, or a hybrid material of steel with ceramic proportions. The invention is not limited to a particular material, so long as this material is able to crush mineral material with sufficient service life.
- The trapezoidal longitudinal ribs have each two flanks which extend from the base to the topside. The confronting inner flanks of adjacent longitudinal ribs define a flank angle of 20° to 27° in relation to the x axis. In particular the flank angle is 23° to 26° and preferably 25°. This flank angle has proven to be especially appropriate for the transmission of forces from the impact bar onto the rotor and for the transmission of the torque from the rotor onto the impact bar.
- Preferably, not only are the flank angles of both inner flanks on a length side identical but also the flank angles of both outer flanks. In addition, the flank angles of the inner and outer flanks can be identical and also amount to 20° to 27°, in particular 23° to 26°, preferably 25°.
- The outer flanks have this angle that deviates by approx. 25° from the x axis so that the forces introduced into the longitudinal ribs have to be deflected at the transition from the base to the flanks not by 90° but rather by about 65°. In addition, the transitions of the flanks to the base are rounded, a fact that also prevents stress peaks in the material.
- The impact bar has a width which is measured in x direction and is at least as great between the longitudinal ribs as the width in the region of the end faces. Preferably, the width between the longitudinal ribs is greater than the width in the region of the end faces, in particular in the magnitude of 4 to 10%. The width of the impact bar in the impact zone deviates only relatively slightly from the width between the longitudinal ribs, e.g. 80 mm/85 mm or 100 mm/108 mm (width end faces/width between the longitudinal ribs). The greater width between the longitudinal ribs is appropriate because the longitudinal ribs are exposed to higher loads, when the force is introduced in the manner according to the invention and because the loads on the longitudinal ribs should be transmitted onto the further longitudinal ribs via the central region of the impact bar with as little stress as possible. The central region of the impact bar between the longitudinal ribs should therefore have a greater width.
- The invention is based on the fact that the width of an impact bar that is not worn off is substantially constant in both the region of the end faces and between the longitudinal ribs.
- The holding region relates within the scope of the invention to the one region in which the impact bar is clamped. It begins on an upper contact zone at the outer longitudinal rib and ends on a lower contact zone at the lower longitudinal rib. The impact bar is clamped between the longitudinal ribs through formfitting engagement.
- The invention avoids a weakening of the cross section of the impact bar as a result of lateral notches. The different widths effect that the central region between the longitudinal ribs appear like a depression, when in fact the cross section of the impact bar is not weakened but rather even reinforced. The is no notch effect. The provision of more material in the central region creates the basis for a secure anchoring of a turnable impact bar. The combination of the slightly wider central region with these flank angles of the inner flanks enables an impact bar which requires as a result less material while having higher stress resistance and therefore attains a high utilization factor of at least 50%. Preferably, the utilization factor is greater than 55% and in particular greater than 60%.
- As a result of the width differences, the confronting inner flanks of the longitudinal ribs are shorter than the outer flanks, so long as the inner and outer flanks have the same flank angle. During operation, centrifugal forces are transmitted via the inner flanks of the radially inner longitudinal ribs onto the impact bar clamps in the impact bar mount. The impact bars effect very high centrifugal forces due to their high own weight and high rotation speeds. The formfitting engagement between rotor and impact bars effects a secure fixation in radial direction of the rotor. Still, the impact bars can be replaced at standstill in a mechanically simple manner because of their sole contact with the rotor via the flanks of the longitudinal ribs. The impact bars may be pulled out of the impact bar mounts. As the axial stress is fairly slight, simple fixing means are sufficient to effect the axial securement, such as, e.g. axial safeguards that are screwed onto the rotor. They are easy to detach and enable a direct access to the impact bar.
- The impact bar mount is bordered on both sided by impact bar clamps. The impact bar clamps are welded to the rotor. The rotor may be constructed from several rotor disks arranged in parallel relationship, with the impact bar clamps extending from rotor disk to rotor disk. The impact bar clamps are those components with which the impact bars are in contact via their flanks.
- The inner flanks of the radially inner longitudinal ribs are not exposed to stress by the centrifugal forces but primarily by the fact that the material to be comminuted impacts the impact bar and is greatly accelerated by the impact bar. As the impact circle of the rotor is greater than the rotor itself, torque is exerted upon the impact bar. This torque is transmitted via the flanks of the longitudinal ribs into the rotor. Conversely, the driven rotor transmits forces into the impact bar clamps which in turn transmit the forces via these flanks into the longitudinal ribs of the impact bar. The inner confronting flanks of the longitudinal ribs are in addition to the impact surfaces the most important surfaces of the impact bars as they, and only they in accordance with the invention, participate in the force transmission. It is not excluded within the scope of the invention for the mineral material that has penetrated gaps and joints between impact bar and impact bar clamp to effect an additional or indirect force transmission. The forces are transmitted predominantly via the flanks.
- As the material breaks, primarily the radially inner flank of the radially outer longitudinal rib is under stress on the backside of the impact bar. On the front side, it is the inner flank of the radially inner longitudinal rib during breakage. In accordance with the invention, the flanks are oriented such that the torques to be absorbed impact about the longitudinal axis (rotation axis/z axis) onto surfaces which extend in radial direction towards the rotation axis. Ideally is when these surfaces are spaced at great radial distance to the rotation axis. The lever arm is increased and as a result surface pressure is reduced at the support point, i.e. the force vector becomes smaller. In accordance with the invention, a great lever arm is established while the impact bar is slender, when the flanks providing support points or support surfaces have a great radial distance from the longitudinal axis (z axis). So that the utilization factor remains high at the same time, the longitudinal ribs may not be too wide/high. Optimally, the flanks are arranged at an angle of 20° to 27° and lie in a radial; plane which intersects the longitudinal axis. Due to the symmetry, the intersecting radial planes of the four inner flanks extend at an angle of 2×20°-27° =40°-52° in relation to one another, preferable 50°. The inner flanks are arranged virtually x-shaped in relation to the center point of the impact bar or z axis, about which the torque is applied and which lie in the same plane in which the diametrically arranged inner flanks are located.
- In final analysis, the introduced torques are absorbed in this configuration by the impact bar clamps in an optimum manner. Bending moments in the longitudinal ribs are reduced and wear as well as material stress are diminished. Risk of breakage decreases so that the central region between the longitudinal ribs can be configured smaller in relation to the overall impact bar, thereby enhancing the utilization factor.
- In the installation position, both radially outer flanks can form a shoulder for protection of adjacent components of the rotor. The radially outer flanks may for this purpose wear off to a certain degree. This does not adversely affect the function of the impact bar because the outer flanks have no contact areas with the rotor. A deviation of the dimensional precision or wear in this region does not impair the secure fit or service life of the impact bar.
- A geometry of the impact bar is viewed as especially beneficial, when the ratio between the width of the impact zone and the minimum distance of the flanks in the central region is 1.8-2.2 to 1, in particular 2 to 1. This width in the impact zone is preferably greater than 70 to 80 mm. The width is in particular constant across the entire impact zone.
- The ratio between the minimum distance of the inner flanks between the longitudinal ribs and the height of the longitudinal ribs is preferably 1.8-2.2 to 1, in particular 2 to 1.
- The longitudinal ribs should have a width in x direction of 40%-60%, in particular 50%, in relation to the height of the impact bar. Their topsides should have a height in y direction of preferably 40%-60%, in particular 50%, in relation to the minimum distance of the inner flanks between the longitudinal ribs. The width of the impact bar in the region of the longitudinal ribs is greater by preferably 40%-60%, in particular 50%, than the width of the impact bar in the impact zone. The length of the impact bar in z direction is independent on other proportions.
- The invention proposes for securement an appropriate rotor in which the impact bar mount includes opposing impact bar clamps with projections in order to engage between the longitudinal ribs. The projections have in this case the same flank angles as the inner flanks of the longitudinal ribs. As a result, the surface pressure is kept as small as possible, that is on both the rotor and the impact bar. The material is used in an optimum manner while stress is even. Thus, material can be saved on the rotor and on the impact bar.
- According to an advantageous refinement of the invention, protective rotor plates are arranged on the rotor to radially cover the impact bar clamps about their circumference. The protective rotor plates are replaceable wear parts, which, however, have a much longer service life than the impact bars, because they are exposed to less stress. The protective rotor plates can be placed in accordance with the invention in very close proximity to the impact bar. A border side of a protective rotor plate is arranged preferably directly in opposition to the topsides of the radially outer longitudinal ribs. Thus, the topsides of the radially outer longitudinal ribs, up to which topsides the end faces wear off, are protected in an optimum manner, so that the impact bars can wear off in a maximum manner without damage to their longitudinal ribs.
- The contact zone between the impact bar and the impact bar clamps is very limited in height. The radially innermost contact zones between the impact bar and the impact bar clamps are situated at the inner flanks of the radially inner longitudinal ribs. Conversely, the radially outermost contact zones between the impact bar and the impact bar clamp are situated at the inner flank of the radially outer longitudinal ribs. Although the contact zone between rotor and impact bar is very concentrated; still the diametric disposition of the flanks as support faces and the resultant greater lever arms are able to transmit very large forces and torques.
- In accordance with a refinement of the invention, the impact bar mount can include a radially inner region for receiving the second end face or second impact section of the impact bar, with this region widening in x direction, and a region which is narrower in x direction and situated between the projections. It is located further radially outwards. A rounded transition zone is arranged between these regions and extends across at least 50% of the width of the topside of the inner longitudinal ribs. The rounded zone is very large so as to prevent as much as possible formation of notch stress in this region. The topsides of the longitudinal ribs do not touch the inner regions of the impact bar mount and therefore do not transmit any forces. In view of the longitudinal ribs that directly confront one another in pairs, broad shoulder belts are established which transmit the centrifugal forces of the impact bar into the rotor.
- The impact bar according to the invention has the following advantages:
- In the installation position, the confronting radially outer longitudinal ribs form a region of maximum width as shoulder belt. The greatest torques of the impact bar are applied at the radially outer shoulder belt. They are effectively introduced into the adjacent regions as a result of the optimized flank geometries. The broad shoulder also protects the rotor itself even against wear.
- The impact bar is profiled in a simple manner, has clear proportions and therefore is cost-effectively to produce.
- The impact bar has a greatest possible support width due to the diametrically arranged flanks of orientation in same direction, so that stress on the impact bar is reduced.
- The greatest possible radius in the impact bar mount prevents stress peaks in the impact bar clamp and provides highest stability.
- The flank angle of approx. 20 to 27°, preferably 25°, has the advantage that the deflection forces within the impact bar mount are small. As the flank angle increases, also the deflection forces would increase, i.e. the forces that act transversely to the impact bar mount. Flank angles below 20° would enlarge the width of the impact bar, when the radial distance of the flanks remains the same, thereby decreasing the utilization factor. When the width should not be made greater, the radial distance of the flanks needs to be made smaller, resulting in shorter lever arms and higher surface pressure. The range between 20′ and 27° has been viewed as optimal.
- Forces acting on the impact bar are introduced via the radially inner longitudinal ribs at these flank angles far inside the rotor interior into the rotor. This reduces stress on the outer circumferential area of the rotor and improves material usage.
- The rotor may be equipped with two, three or more identical impact bars which are evenly dispersed about the circumference. It is also possible to combine impact bars of different height, e.g. two impact bars of greater height with two impact bars of smaller height in alternating disposition. The impact bars find application in particular in reversible impact crushers. Use in non-reversible impact crushers is also possible.
- Exemplary embodiments of the invention will be described hereinafter in greater detail with reference to purely schematic drawings.
- It is shown in:
-
FIG. 1 a plan view of a rotor of an impact crusher; -
FIG. 2 a section through the rotor ofFIG. 1 along the line II ofFIG. 1 ; -
FIG. 3 a detail III ofFIG. 3 ; and -
FIG. 4 a cross section of an impact bar. -
FIG. 1 shows arotor 1 of an otherwise not shown impact crusher. Therotor 1 includes ahorizontal rotor shaft 2 which is mounted inbearings rotor shaft 2 extends horizontally between thebearings pulley 5. Impact bars 6 are dispersed about the circumference of therotor 1. Theuppermost impact bar 6 in the drawing plane ofFIG. 1 extends like allother impact bars 6 in parallel relation to the rotation axis D of therotor shaft 2. - The following description of the impact bars 6 relates to a Cartesian coordinate system. The origin of the coordinate system is situated in the middle of the
impact bar 6, i.e. at half length (z axis), height (y axis) and width (x axis) of thisimpact bar 6. Referring to theimpact bar 6 which is uppermost in the drawing plane and perpendicular to the rotation axis D, the x direction extends tangentially to therotor 1. The y axis is the radial direction and points away from therotor shaft 2. The z axis extends parallel to the rotation axis D. - As is apparent from the sectional view of
FIG. 2 , a total of fourimpact bars 6 are evenly dispersed about the circumference of therotor 1. The fourimpact bars 6 are identical, as are the associated impact bar mounts 7 within therotor 1. The impact bar mounts 7 represent pockets that extend in length direction of the rotor, i.e. parallel to the rotation axis D of therotor shaft 2. With reference to the coordinate system introduced inFIG. 1 , the pockets extend in z direction. - The impact bars 6 are configured in cross section substantially rectangular. With reference to the y-z plane and also with reference to the x-z plane, the impact bars are mirror images. They have each radial head faces which extend in substantial parallel relation to the x-z plane. As the impact bars 6 involve cast parts, the head faces 8 may have a slight draft as caused by casting. The length sides 9, 10 of the
impact bar 6 extend at a parallel distance to one another and as a result extend substantially perpendicular to the head faces 8. - Two terminal end faces 11, 12, 13, 14 are situated at the length sides 9, 10 and provide impact surfaces. Provided between the end faces 11-14 of each
length side 9, 10 are undercuts, respectively, which are designated as holdingregions regions longitudinal ribs FIGS. 2 to 4 . All longitudinal ribs 17-20 are of identical configuration and have the same cross section. The longitudinal ribs 17-20 have a trapezoidal cross section and a have awider base 21 and a narrower topside 22 (FIG. 4 ). Inclined flanks extend between the base 21 and thetopside 22. Inner flanks 23-26 confront one another and limit the holdingregions - Arrow P1 in
FIG. 2 symbolizes the rotation direction of therotor shaft 2 and thus of therotor 1. Due to the rotation direction, theend face 11 represents the impact surface that is subject to stress. At this rotation direction, also the designations front side and backside of theimpact bar 6 could be used. As the rotation direction is reversible, theopposite end face 14 may likewise serve as impact surface, when operation is reversed. - A rotary movement is transmitted via the
rotor 1 and the impact bar mounts 17 onto the impact bars 6. The impact bars 6 are pushed into the impact bar mounts 7 in a manner not shown in greater detail in z direction, i.e. in length direction of therotor 1. The impact bars are secured in the installation position against axial displacement. As a result of the formfitting engagement of impact bar clamps 28, 29 between the longitudinal ribs 17-20, the impact bars 6 are held captive in therotor 1. The impact bar clamps 28, 29 rest upon the inner flanks 23-26 of theimpact bar 6, respectively. Due to the inclined inner flanks 23-26, the undercut region, i.e. the respective holdingregion - As becomes apparent from the enlarged illustration of
FIG. 3 , a contact zone is established between the flanks 23-26 and the impact bar clamps 28, 29. The impact bar clamps 28, 29 have for that purpose opposingidentical projections FIG. 4 . -
FIG. 3 shows that the radially outermost contact zone between the impact bar clamps 28, 29 and theimpact bar 6 is formed by the radiallyinner flanks longitudinal ribs inner flanks respective projections longitudinal ribs rotor 1. They are protected byprotective rotor plates 32 which are screwed onto therotor 1 radially from outside. Theprotective rotor plates 32 cover the impact bar clamps 28, 29 and protect them against wear. Theprotective rotor plates 32 have each aborder side 33 which confronts thetopsides 22 of thelongitudinal ribs longitudinal ribs protective rotor plates 32 are detachably secured. -
FIG. 3 shows an enlarged view of the area Ill according toFIG. 2 . Various wear lines are plotted in the radially outer part of theimpact bar 6. The wear lines show that therotor 1 has been operated at the beginning counterclockwise, since the left upper corner of theimpact bar 6 has been stripped off at first. Subsequently, the rotation direction has been reversed, so that theend face 11 on the right-hand side of the drawing plane serves as impact surface. Thus, the right upper corner of theimpact bar 6 has been stripped. After multiple reversals of therotor 1, the wear limit V has been reached. The wear limit V is located approximately in prolongation of the radiallyouter flanks 27. The wear limit V is the limit for maximum use of theimpact bar 6. Theimpact bar 6 has in this state an approximately triangular remaining cross section at the wear limit V. - When the wear limit V has ultimately been reached, the
impact bar 6 is pulled out of theimpact bar mount 7 in length direction of therotor 1 and can be turned about its length axis, so that the previously inner end faces 13, 14 now face outwards. There is no preferential direction of theimpact bar 6, when turning by 180 degrees. It is irrelevant, whether theimpact bar 6 is turned about its length axis only, or turned at the same time during turning about its vertical axis. The rotational symmetry of theimpact bar 6 enables both insertion directions into theimpact bar mount 7. -
FIG. 3 shows that theimpact bar mount 7 is configured relatively wide in the region of theimpact bar 6 that is not in engagement. In theimpact bar mount 7, there is aninner region 34 which is widened in x direction. The width of thisinner region 34 is greater than the width of theimpact bar 6, measured across thelongitudinal ribs region 35 that is narrower in x direction is situated between theprojections wider region 34 is connected to thenarrower region 35 by atransition zone 36. Thetransition zone 36 is rounded. Rounding of the transition.zone 36 extends across at least 50% of the height of thetopside 22 of the inner longitudinal ribs. The provision of the great rounding radius prevents stress in this region of the impact bar clamps 28, 29. This is important because this region of the impact bar clamps 28, 29 needs to absorb not only the centrifugal forces that are exerted from theimpact bar 6 onto therotor 1 but also because the torque of therotor 1 has to be transmitted from the impact bars 6 onto the material being comminuted. The impact bar according to the invention includes for this purpose special proportions which will be described hereinafter with reference toFIG. 4 . - The
impact bar 6 includes in this exemplary embodiment a height H1 of 320 mm at a width B1 in its impact zone of 80 mm. The ratio of height to width is 4:1. - The
impact bar 6 is slightly wider in its mid mounting portion that is not subject to wear than in the impact zone. The longitudinal ribs 17-20 have each a height of 20 mm, measured from the terminal end faces 11-14 (width B2). Theirtopsides 22 have a height H2 of 20 mm. The height H3 is measured at thebase 21 and indicates the minimum distance of the inner flanks 23-26 of the longitudinal ribs 17-20. -
FIG. 4 further shows that the flank angles W1 are identical for all plotted flanks of the longitudinal ribs 17-20. They amount to 25 degree. The inner flanks 23-26 extend each radially from a center point M of theimpact bar 6. Thus, the illustrated dash-dot lines intersect as prolongation of the respective inner flanks 23-26 in the center point M. The center point M lies on the length axis of the impact bar 6 (z axis), about which the mountedimpact bar 6 can theoretically swing within theimpact bar mount 7 during operation within the scope of the provided tolerances. - When a clockwise rotation direction of the
rotor 1 is involved, i.e. in direction of arrow P1 (FIG. 2 ), a force originating fromrotor 1 is applied onto theinner flanks inner flanks longitudinal ribs impact bar 6 in position. The centrifugal forces of theimpact bar 6 are absorbed there. When impacting material exerts a force onto theend face 11, predominantly the upperlongitudinal rib 19 on the left-hand side of the drawing plane and in addition thelongitudinal rib 18 on the lower right-hand side are exposed to stress, because a torque in direction of arrow P2 about the center point M is applied upon theimpact bar 6. The resultant forces are taken up via theseinner flanks -
FIG. 4 further shows that the width B3 of theimpact bar 6, which is measured across thetopsides 22 of thelongitudinal ribs impact bar 6 in the region of its impact zone. In the holdingregion impact bar 6, the width B4 is sized at least as the width B1 in the region of the end faces 11, 12, thereby preventing the presence of any notch as material weakening. In this exemplary embodiment, the width B4 in the region between the longitudinal ribs 17-20 is 85 mm as compared to 80 mm in the impact zones. - 1—rotor
- 2—rotor shaft
- 3—bearing
- 4—bearing
- 5—pulley
- 6—impact bar
- 7—impact bar mount of 1
- 8—head face of 6
- 9—length side of 6
- 10—length side of 6
- 11—end face of 6
- 12—end face of 6
- 13—end face of 6
- 14—end face of 6
- 15—holding region of 6
- 16—holding region of 6
- 17—longitudinal rib of 6
- 18—longitudinal rib of 6
- 19—longitudinal rib of 6
- 20—longitudinal rib of 6
- 21—base
- 22—topside of 17-20
- 23—inner flank of 17
- 24—inner flank of 19
- 25—inner flank of 18
- 26—inner flank of 20
- 27—outer flank of 17-20
- 28—impact bar clamp of 1
- 29—impact bar clamp of 1
- 30—projection of 29
- 31—projection of 28
- 32—protective rotor plate of 1
- 33—border side of 32
- 34—holding region of 7
- 35—narrower region of 7
- 36—transition zone between 34 and 35
- B1—with between 11 and 14
- B2—width of 17-20
- B3—with between 18 and 20
- B4—with between 15 and 16
- D—rotation axis
- H1—height of 6
- H2—height of 17-20
- H3—minimum distance between 23-26 at the
base 21 - M center point of 6
- P1—rotation direction
- P2 torque
- V—wear limit
- W1—angle
- x, y, z—axes of the coordinate system of 6
- The invention relates to an impact bar for installation in an axis-parallel impact bar mount (7) of a rotor (1) of an impact crusher with following features:
-
- a. The
impact bar 6 includes within a Cartesian coordinate system a longitudinal axis which extends in z direction in parallel relation to theimpact bar mount 7 in the installation position, a vertical axis which extends in y direction and is directed towards aradial head face 8 of theimpact bar 6, and a transverse axis which extends in x direction and is directed towards a length side 9 of theimpact bar 6; - b. The
impact bar 6 includes on each of itslength sides 9, 10 two terminal end faces 11, 12, 13, 14 and a front-side and abackside holding region regions longitudinal ribs longitudinal ribs - c. The
longitudinal ribs wider base 21 at theimpact bar 6 and anarrower topside 22 at a distance to thebase 21, and respectively have an innerinclined flank outer flank 27, with theflanks 23 to 27 extending between the base and the topside 22 and with theinner flanks - d. Only the
inner flanks impact bar mount 7 at therotor 1.
- a. The
Claims (21)
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DE102017113238.4A DE102017113238B4 (en) | 2017-06-16 | 2017-06-16 | Blow bar, rotor and impact crusher |
DE102017113238.4 | 2017-06-16 | ||
DE102017113238 | 2017-06-16 |
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US20190015838A1 true US20190015838A1 (en) | 2019-01-17 |
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US16/010,048 Active 2038-10-17 US10792664B2 (en) | 2017-06-16 | 2018-06-15 | Impact bar |
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US (1) | US10792664B2 (en) |
EP (1) | EP3415236B1 (en) |
CN (1) | CN109127001B (en) |
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ES (1) | ES2773715T3 (en) |
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CN109999957B (en) * | 2019-03-07 | 2021-07-30 | 孙红勤 | Multistage vertical crusher |
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2017
- 2017-06-16 DE DE102017113238.4A patent/DE102017113238B4/en not_active Expired - Fee Related
-
2018
- 2018-06-15 ES ES18177911T patent/ES2773715T3/en active Active
- 2018-06-15 EP EP18177911.7A patent/EP3415236B1/en active Active
- 2018-06-15 US US16/010,048 patent/US10792664B2/en active Active
- 2018-06-15 PL PL18177911T patent/PL3415236T3/en unknown
- 2018-06-15 LT LTEP18177911.7T patent/LT3415236T/en unknown
- 2018-06-19 CN CN201810628223.0A patent/CN109127001B/en active Active
Patent Citations (16)
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US2588434A (en) * | 1949-06-16 | 1952-03-11 | Frank P Unti | Impact bar assembly for impeller breakers |
US2635817A (en) * | 1950-08-21 | 1953-04-21 | Leo H Long | Impact breaker bar mechanism |
US2747803A (en) * | 1952-07-09 | 1956-05-29 | Pettibone Mulliken Corp | Hammer rotor for hammermills |
US3236463A (en) * | 1964-01-08 | 1966-02-22 | American Brake Shoe Co | Centrifugal hammer and renewable tip |
US3510076A (en) * | 1966-12-27 | 1970-05-05 | Esco Corp | Impact device |
US3608841A (en) * | 1968-03-14 | 1971-09-28 | Franz Wageneder | Rotary impact crusher |
US3838826A (en) * | 1972-09-27 | 1974-10-01 | Capeletti Bros Inc | Removable caps for crusher hammer assembly |
US3929296A (en) * | 1973-04-07 | 1975-12-30 | Hans Stoeber | Striking tool |
US3979078A (en) * | 1974-03-15 | 1976-09-07 | Hazemag Dr. E. Andreas Kg | Beater bar for rotors of impact mills |
US4180213A (en) * | 1978-04-12 | 1979-12-25 | Matsuzaka Company Ltd. | Rotor of a coarse-reduction impact crusher |
US4373678A (en) * | 1980-06-30 | 1983-02-15 | Reitter Guenther W | Rotary impact crusher having a continuous rotary circumference |
US4714207A (en) * | 1985-07-17 | 1987-12-22 | Fried. Krupp Gesellschaft Mit Beschrankter Haftung | Impact bar for a comminuting rotor |
US4915309A (en) * | 1987-12-15 | 1990-04-10 | Deutscher Sbm Vertrieb Franz Wageneder | Rotor for a rebound crusher |
US4848682A (en) * | 1988-05-31 | 1989-07-18 | Morris Scheler | Double bladed rock crusher |
US5111569A (en) * | 1989-11-22 | 1992-05-12 | Cedarapids, Inc. | Method of locking an impeller bar against a seat |
US6845933B2 (en) * | 2002-01-09 | 2005-01-25 | Cedarapids, Inc. | Impeller bar retaining wedge assembly and rotor employing the same |
Also Published As
Publication number | Publication date |
---|---|
CN109127001A (en) | 2019-01-04 |
PL3415236T3 (en) | 2020-06-29 |
US10792664B2 (en) | 2020-10-06 |
ES2773715T3 (en) | 2020-07-14 |
DE102017113238A1 (en) | 2018-12-20 |
DE102017113238B4 (en) | 2020-09-24 |
CN109127001B (en) | 2020-10-27 |
EP3415236B1 (en) | 2019-11-20 |
LT3415236T (en) | 2020-05-25 |
EP3415236A1 (en) | 2018-12-19 |
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